Drilling machine with pneumatic control

ABSTRACT

A pneumatic drilling machine is provided, comprising a pneumatic motor, a circuit for connecting the motor to a source of compressed air, a tool holder spindle, and a drive mechanism. The drive mechanism comprises a coupling shaft which can be moved to select a first mode of driving the spindle and a second method of driving the spindle. The mechanism has a driving cycle which comprises a stationary mode at the beginning and end of the cycle, and at least one phase for driving the spindle according to the first driving method, then a phase for driving the spindle according to the second driving method, then the stopping of the supply of air to the motor. A supply valve of the circuit is controlled pneumatically by the drive mechanism to interrupt the supply of compressed air to the motor at the end of the driving cycle.

FIELD OF THE INVENTION

The present invention relates to the field of pneumatic drillingmachines, more specifically, pneumatic drilling machines whichautomatically terminate the supply of compressed air to the machineafter a drilling cycle is complete.

BACKGROUND OF THE INVENTION

Positive feed pneumatic power drilling machines are widely used in manyindustries. Such drilling machines normally have a single motor forturning a spindle through a drive gear train. The spindle is threadedinto a feed gear that turns at a predetermined rate faster than theturning rate of the spindle for advancing the spindle as the drillprogresses through a work piece. The feed gear is driven by a gear trainfrom the same motor as the drive gear train. The gear ratio of the drivegear train is selected to be slightly less than the gear ratio of thefeed gear train so the feed gear will turn slightly faster than thedrive gear. In that way, the spindle is advanced a predetermined amountfor each turn. Once the spindle has been advanced sufficiently, amechanism is actuated to disengage the spindle feed gear train from themotor and lock it in place. As the motor continues to drive the spindlein the same direction, the spindle threads turn inside the locked feedgear to rapidly retract the spindle.

Prior art mechanisms for disengaging the gear trains from the motor haveincluded mechanical switches for interrupting the supply of compressedair to the motor. The inclusion of mechanical switches in a pneumaticdrilling machine have certain disadvantages. First, they are difficultto assemble, requiring delicate placement of the moving parts within theswitch. Further, the delicate parts of the switch are prone to wear andtear, and detract from the longevity of the drilling machine as a whole,which otherwise benefits from a reduction in the number of moving partsthat pneumatic tools generally provide.

Another aspect of prior art drilling machines is that they includepneumatic counting devices, for counting the number of drive cyclescarried out by the machine. This allows the owner to carry out therequired maintenance on the machine at a proper interval. However, afeature of the prior art counters is that they typically have beenconfigured to add one cycle to the total count each time the motor isswitched on. This is disadvantageous because a drill user will oftenturn the drill off, and then on again, a number of times in the middleof the feed mode. Thus, a single feed cycle may be counted as a numberof cycles. This has the undesirable effect of indicating that the drillhas been used more often than it really has been, and leads touneconomical servicing of the machine.

Thus, a need exists in the art for a pneumatic drill with apneumatically operated switch for turning off the motor. A need alsoexists for a counting system that counts feed cycles of the drill onlyat the completion of a feed cycle. It is believed that the presentinvention addresses these and other needs.

SUMMARY OF THE INVENTION

According to a preferred embodiment of the invention a pneumaticdrilling machine with an automatic control system is described.

In a preferred embodiment, the drilling machine comprises a pneumaticmotor, a tool holder spindle, and a drive mechanism connecting the motorto the spindle. The drive mechanism is configured to drive the spindlethrough a driving cycle, the driving cycle commencing and ending withthe spindle being stationary. The driving cycle also includes a feedmode and a retraction mode.

In a preferred embodiment, the drive mechanism will include a pneumaticcircuit and a control valve positioned in the circuit. The control valveis movable between a first position to select the feed mode, and asecond position to select the retraction mode.

A supply valve is provided, positioned in the pneumatic circuit forsupplying compressed air to the motor. The supply valve is movablebetween a closed position in which compressed air to the motor isinterrupted and an open position in which air to the motor is supplied.A coupling shaft is also provided for changing the driving mode of thedriving mechanism. The coupling shaft is axially biased by a couplingspring into a coupling chamber positioned in the pneumatic circuit.

The drive mechanism is configured to send, at the end of the drivingcycle, a pneumatic signal to the supply valve via the pneumatic circuit,and the supply valve is configured to close upon receiving the pneumaticsignal. In a preferred embodiment, the pneumatic signal is a bolus ofair expelled from the coupling chamber by the bias of the couplingspring.

Another aspect of the invention is that the pneumatic circuit includes aconnector for receiving compressed air, and the control valve isconfigured in relation to the pneumatic circuit so that, when thecontrol valve is in the first position the coupling chamber is not opento the connector via the pneumatic circuit, but is open to the shut-offchamber. Yet another aspect of the invention is that the control valveis configured in relation to the pneumatic circuit so that, when thecontrol valve is in the second position the coupling chamber is open tothe connector via the pneumatic circuit, but is not open to the shut-offchamber.

A still further aspect of the invention is that the supply valveincludes a shut-off piston positioned within a shut-off chamber and thecoupling shaft includes a coupling piston positioned within the couplingchamber. In a preferred embodiment, the diameter of the shut-off pistonis at least twice as large as the diameter of the coupling piston. Inthis embodiment, the bolus of air expelled from the coupling chamber isdirected by the pneumatic circuit to the shut-off chamber of the supplyvalve. The bolus of air raises the pressure in the shut-off chamber toclose the supply valve, and hence interrupt the supply of air to themotor.

A further feature of the invention is that the drive mechanism furtherincludes a cycle counter configured to add one count only at thecommencement of a retraction mode of driving the spindle.

These and other advantages of the invention will become more apparentfrom the following detailed description thereof and the accompanyingexemplary drawings.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 represents a perspective view of a portable pneumatic drillingmachine showing features of the invention.

FIG. 2 is a schematic view showing aspects of a driving mechanism whichcontrols the power supply and automatic shutoff of compressed air supplyto the drilling machine of FIG. 1, schematically showing aspects of thedrive mechanism in standby mode.

FIG. 3 is the schematic view of the preceding Figure, schematicallyshowing aspects of the drive mechanism in idle mode.

FIG. 4 is the schematic view of the preceding Figures, schematicallyshowing aspects of the drive mechanism in feed mode.

FIG. 5 is the schematic view of the preceding Figures, schematicallyshowing aspects of the drive mechanism in retraction mode.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

With reference to FIG. 1, a pneumatic drilling machine, generallyreferred to by the numeral 20, and method according to a preferredembodiment of the present invention, is described. In general terms, themachine 20 illustrated in the figure is surrounded by a housing 22 andincludes a conventional pneumatic motor 24. The motor is connectable toan external source of compressed air 25 (not shown in FIG. 1) through aconnector 26. A tool holder spindle 28 held by the housing 22 is adaptedto be rotatable about its axis A, and to move the tool back and forthalong its axis A. A mechanism 30 for driving the spindle and forcontrolling the movement of the spindle 28 is located within thehousing. Drilling tools can be mounted and removed from the spindle in aconventional manner.

The drive mechanism 30, which is schematically exemplified in FIGS. 2-5,includes a conventional mechanism known as a positive feed drill. Anexternal source of compressed air 25 supplies compressed air to thedrive mechanism 30 via the connector 26. Within the drilling machinehousing, the compressed air is circulated, as described herein, througha series of ducts which collectively form a pneumatic circuit. FIGS. 2-5exemplify additional features of the present invention, and, in thedescription below, the terms “lower,” “upper,” “horizontal,” “left,” and“right” relate to FIGS. 2-5.

In a preferred embodiment, the drive mechanism 30 includes a lower gear(or, drive gear) train 32 comprising gears 34, 36, 38, 40, and 42intermeshing in series, and an upper gear (or, feed gear) train 44comprising gears 46, 48, 50, and 52 intermeshing in series. The spindle28 passes through the end gears 42 and 52 of each gear train. The lowerand upper gear trains may be stationary, or rotate in various modes, asdescribed herein.

In the idling mode, power is supplied via the motor 24 to lower gear 34,which imparts power only to the lower gear train 32. In this mode, theupper gear train 44 rotates only under frictional connection with thelower gear train 32, so that lower and upper gear trains rotate at thesame speeds, causing the spindle to rotate under power, but not causingthe spindle to advance or retract along its axis A.

In the feed, or advancing, mode, lower gear 34 is supplied with powerfrom the motor 24 as before, but upper gear 46 is caused (as describedherein below) to engage via conventional dog collar linkage to lowergear 36, thus placing both upper and lower gear trains under power. Thenumber of teeth of upper and lower gear trains are selected to differ bypreferably one or two teeth, causing the upper (feed) gear 52 to rotateabout the spindle 28 at a slightly faster speed than lower (drive) gear42. By conventional means, this difference in rotation speeds isharnessed to cause the spindle 28 to advance downwardly at a relativelyslow speed through the upper end gear 52 and the lower end gear 42,while simultaneously rotating clockwise.

In the retraction mode, lower gear 34 is supplied with power from themotor as before, but upper coupling gear 46 is caused (as describedherein below) to move upward to engage by conventional dog collar meansa braking disc 54 which is fixed to the housing and unable to rotate. Itwill be appreciated that, under these conditions, the upper gear 44train cannot rotate at all. It will be further appreciated that in thismode the lower gear train 32 will rotate faster than the upper geartrain by a relatively large difference. By conventional means, thislarge difference in rotation speeds is harnessed to cause the spindle 28to retract at a relatively rapid rate through the upper end feed gear 52and the lower end drive gear 42, while simultaneously rotatingclockwise.

A further aspect of the drive mechanism 30 is the supply valve 56positioned between the external compressed air supply 25 and the motor24. The supply valve 56 includes a shaped slide 58 movable within acylinder 60. The top of the cylinder 60 may be connected by air duct 61to a micro valve 63 that presents an exposed surface or button 62 formanually activating the micro valve 63 which, in turn, activates thesupply valve 56. The slide 58 is configured so that, upon downwarddisplacement (FIGS. 3-5), it will permit the passage of compressed airfrom the source 25 via duct 59 through the valve 56 to the motor 24. Atthe lower end of the supply valve 56 is a shut-off piston 64 connectedto the slide 58. The shutoff piston 64 resides within a shut-off chamber66. A sufficient pressure in the shut-off chamber 66 is capable oflifting the shut-off piston 64 and slide 58 upwards to interrupt thesupply of compressed air to the motor 24. (FIG. 2)

Yet another aspect of the drive mechanism 30 is the coupling shaft 68which is configured to rotate in, and slide through, lower coupling gear36 and to rotate in, but to be translationally connected with, uppercoupling gear 46. Thus, any translational movement of the coupling shaft68 will translationally carry upper gear 46 with it. A coupling spring70 is positioned to bias the coupling shaft 68 downward. Adjacent thecoupling shaft is an idler lock 72, having an arm 74 configured toremovably engage with an indent 76 in the coupling shaft 68. A torsionspring 78 torsionally biases the idler lock 72. Fixed above the uppergear 46 is the braking disc 54 fixed to the housing and unable torotate, so that an upward movement of the coupling shaft 68 engagesupper gear 46 with the braking disc 54, a downward movement of thecoupling shaft engages gear 46 with gear 36. In an intermediateposition, the coupling shaft 68 is free from connection with either thebrake disc 54 or the lower gear 34. Connected to the lower end of thecoupling shaft 68 is a coupling piston 80 residing within a couplingchamber 82. A sufficient pressure in the coupling chamber 82 is capableof lifting the coupling piston 80 and coupling shaft 68 against the biasof the spring 70.

Another aspect of the drive mechanism 30 is the control valve 85 thatincludes a shaped stem 86 sliding within a cylinder 88. A supply ofcompressed air is brought directly from the compressed air source 25 tothe control valve 85 by a duct 90. The control cylinder 88 is connectedvia a duct 92 with the coupling chamber 82, and via a duct 94 with theshut-off chamber 66. The control valve 85 is configured to have twomodes, corresponding with two vertical positions of the shaped stem 86within the cylinder 88. In a first mode, the stem 86 is in an upperposition and configured to pneumatically connect the coupling chamber 82with the shut-off chamber 66 via duct 92 and duct 94, but prevent thesupply of compressed air 25 to both the shut-off chamber and the controlchamber, as exemplified in FIG. 2. In a second mode, the stem 86 is in alower position and permits compressed air to be fed from the compressedair source 25 to the coupling chamber 82, but interrupts the pneumaticconnection between the coupling chamber 82 and the shut-off chamber 66,as exemplified in FIG. 5.

The vertical position of the stem 86 of the control valve 85 may be setby movement of the spindle 28, as follows. An upper spindle nut 98 isattached to the spindle 28 so that downward movement of the spindlebrings the upper spindle nut 98 in contact with an upper valve arm 100to move the stem 86 downwards. A lower spindle nut 102 is attached tothe spindle 28 so that upward movement of the spindle brings the lowerspindle nut in contact with a lower valve arm 104 to move the stemupwards.

A further aspect of the drive mechanism is that it includes a pneumaticcounting device 106, pneumatically connected with coupling chamber 82via duct 108. The counting device may be a commercially availablecounting device such as Part No. PM1421 by Ellis/Kuhnke Controls, ofAtlantic Highlands, N.J. 07716. The counting device is adapted to countthe number of drive cycles performed by the drilling machine so thatservice requirements on the machine may be performed as required. Eachtime compressed air is delivered to the coupling chamber 82 (asdescribed herein below), the counting device will add one cycle to thetotal number of cycles counted.

In use, the drilling machine 20 may be operated as follows.

The drive mechanism is initially configured in a standby mode, asschematically represented in FIG. 2. In standby mode, the supply valve56 is closed in a first position, thus interrupting supply of compressedair 25 to the motor 24. The coupling shaft is in an intermediateposition, held in place by the arm 74 on the idler lock 72. The controlvalve 85 is in an upper first position with the slide 86 interruptingsupply of compressed air to the coupling chamber 82.

The standby mode may be followed by the idle mode, as schematicallyrepresented in FIG. 3. The motor is activated by manually depressing thestart button 62. The momentary opening of the micro valve 63 directs anair signal above the slide 58 of the supply valve 56 via the duct 61displacing the slide to open the supply valve, and thus opening thecompressed air supply going to the motor 24, to cause the motor to turnand supply power to lower gear 34, and hence to the entire lower geartrain 32. At this stage the coupling shaft 68 is positioned in anintermediate position so that gear 46 is engaged with neither the brakedisc 54 nor lower gear 36. In this position the drive mechanism 30 is inthe idle mode, with the spindle 28 under rotational or driving powerfrom the lower gear train 32, but not under translational or feedingpower.

The idle mode may be followed by the feed mode, as schematicallyrepresented in FIG. 4. In order to engage the upper gear train 44 toadvance the spindle 28, the idler lock 72 may be turned sufficiently toallow the arm 74 to disengage from the indent 76 in the coupling shaft68. This will allow the coupling shaft 68 under the biasing action ofthe spring 70 to move down and engage the upper coupling gear 46 withthe lower coupling gear 36. The tool now enters the feed, or advancing,mode, with the spindle 28 rotating and being advanced slowly underpower. The feed action of the spindle will continue until the upperspindle nut 98 reaches and pushes down on, the upper valve arm 100 todepress the stem 86 within the cylinder 88 of the control valve 85, asexemplified in FIG. 5, thus leading to the retraction mode, as detailedbelow.

The feed mode may be followed by the retraction mode, as schematicallyrepresented in FIG. 5. The downward movement of the control valve stem86 allows compressed air to flow into the coupling chamber 82, forcingup the coupling piston 80 and hence the coupling shaft 68, therebyending the spindle feed process by disengaging the upper coupling gear46 from lower coupling gear 36, and locking the upper gear 46 againstthe brake disc 54 of the upper housing. The immobilization of the uppergear train 44 will initiate the retraction phase (or return cycle)characterized by a fast return of the spindle (about 1 mm perrevolution), until the lower spindle nut 102 reaches and elevates thelower valve arm 104, returning the valve stem 86 to its first upperposition, as exemplified in FIG. 2, thereby to end the retraction mode,as set forth below.

The return of the valve stem 86 to its first position firstlydisconnects the compressed air supply 25 from the coupling chamber 82(FIG. 2), and, almost simultaneously, connects duct 94 with duct 92,thus pneumatically connecting the coupling chamber 82 with the shut-offchamber 66. It will be appreciated that when the stem 86 was in itssecond lower position, the pressure in duct 94 was around atmosphericpressure, but the pressure in the coupling chamber 82 was undercompression from the source 25, which may be in the region of 90 p.s.i.Thus, when the upward movement of the stem 86 disconnects the couplingchamber 82 from the compressed air supply 25, but connects the couplingchamber 82 to the shut-off chamber 66, the compressed air present in thecoupling chamber 82 is at an elevated pressure (i.e. well aboveatmospheric pressure) and will rapidly discharge into the shut-offchamber 66 until the pressure in both chambers 82 and 66 and theirrelated ducts is equalized. Furthermore, at the same time, the couplingspring 70 biases the coupling piston 80 downwards, adding to the escapeof air from the coupling chamber 82 into the shut-off chamber 66 byexpressing an additional volume, or 37 bolus,” of air (about 0.1 cu.inches) from the coupling chamber 82. It will be appreciated that theresulting upward force applied to the shut-off piston 64 will lift thesupply valve slide 58 to its upper first position (FIG. 2) to cutconnection of the main air supply 25 to the motor 24, thus shutting offthe motor 24. The drive mechanism is now in standby phase, the samecondition it was in prior to pressing button 62. To start the wholecycle over, the user may press button 62 once again.

It will be appreciated that the manner in which the supply valve 56 isclosed, as described in the preferred embodiment, may be accomplished bytransmitting a pneumatic signal directly to the supply valve via thepneumatic circuit within the housing, specifically by the ducts 92, 94.Thus, in a preferred embodiment, the force applied upon the valve 56 tomove it to a closed position is a positive pneumatic force, i.e., aforce not applied by a mechanical action upon the supply valve itself.Moreover, in another aspect, the source of the pneumatic signal mayderive from a fixed quantity of air trapped at elevated pressure withina reservoir located in the drive mechanism. In a preferred embodiment,the reservoir may include the coupling chamber 82, its supply duct 92,and also may include a volume defined by the cycle counting device 106and its supply duct 108 if present. The fixed quantity of air trapped atelevated pressure within a reservoir located in the drive mechanism maybe distinguished over an effectively limitless supply of compressed airfrom the main source of compressed air 25 which is not trapped in thedrive mechanism.

A significant aspect of a preferred embodiment of the invention is thatthe ending position of the slide 86 of the control valve 85 at the endof a drilling cycle is the same as its starting position prior toactivation of the drilling cycle, and that, at both the start and theend of a drilling cycle (as seen in FIG. 2), the main compressed airsupply 25 to the motor 24 is closed by the supply valve 56 and thecompressed air supply to the coupling chamber 82 is closed by thecontrol valve 85, thus giving rise to a completed cycle of operation inall respects. If, for example, the slide 86 connected the compressed airsupply 25 with shut-off chamber 66 upon the upward movement of the slide86 at the end of a drilling cycle, the compressed air has raised theslide 58 to turn off the motor 24. However, it will be appreciated thatcompressed air would now be supplied to the shut-off chamber 66 at thestart of a new drilling cycle, a condition which may prevent the slide58 from being downwardly activated, with disruptive consequences.

An additional aspect of the drilling machine is the emergency valve 110with its activation button 112. The valve 110 is also a micro valve,configured to direct compressed air from the source 25 direct to theshut-off chamber 66 of the supply valve 56 via a duct 114. As will beappreciated, the compressed air in the shut-off chamber 66 will forcethe slide 58 of the supply valve upwards to interrupt air supply to themotor 24. In case of an emergency, depressing the activation button 112will activate the micro valve 110 which in turn will shut off the supplyvalve 56 and the motor 24. A bleed hole in the shutoff chamber 66 allowsfor the decompression of the chamber 66, thus allowing the supply valve56 to be turned on again.

A further significant feature of a preferred embodiment of the inventionis that the cycle counter 106 is pneumatically connected to the couplingchamber 82. This has the advantage that a driving cycle is only countedonce the spindle has completed a feed phase, marked by the advance ofthe control valve 85 to its second position, upon the drive mechanismentering the retraction phase. Accordingly, if the emergency shutoffvalve 110 is activated by pressing emergency button 112 in the middle ofa feeding phase, an additional cycle will not necessarily be added tothe counter when the motor is turned on again. Only upon thecommencement of a retraction phase will the counter add one cycle to thetotal. It will be appreciated that this feature has an advantage oversystems that add one cycle to the total every time the motor is switchedon. In such machines, interrupted but recommenced drive cycles count asa full cycle upon each recommencement, thus biasing the total count to ahigher level than actually carried out by the drilling machine, andleading to uneconomical servicing of the machine or replacing itsaccessories such as drill bits.

Thus, the preferred embodiments of the invention provide for aninexpensive and reliable device and method for automatically controllinga drilling machine. The use of a pneumatic control over the supply valve56, which controls the supply of compressed air to the drive mechanism,eliminates the dangers present in the use of mechanical parts which tendto wear down during the lifetime of a drilling machine. Moreover, apneumatic control system is typically easier to assemble than amechanical control system, and eliminates much of the labor intensiveoperation of assembling the small mechanical pieces of a mechanicalcontrol system.

While a particular form of the invention has been illustrated anddescribed, it will also be apparent to those skilled in the art thatvarious modifications can be made without departing from the spirit andscope of the invention. Accordingly, it is not intended that theinvention be limited except by the appended claims.

1. A pneumatic drilling machine with an automatic control system,comprising: a pneumatic motor; a tool holder spindle; a drive mechanismconnecting the motor to the spindle, the drive mechanism beingconfigured to drive the spindle through a driving cycle, the drivingcycle commencing and ending with the spindle being stationary, thedriving cycle including a feed mode of driving the spindle and aretraction mode of driving the spindle, the drive mechanism including: apneumatic circuit; a control valve positioned in the pneumatic circuit,the control valve being movable between a first position to select thefeed mode of driving the spindle and a second position to select theretraction mode of driving the spindle; and a supply valve positioned inthe pneumatic circuit for supplying compressed air to the motor, thesupply valve being movable between a closed position in which compressedair to the motor is interrupted and an open position in which air to themotor is supplied; wherein the drive mechanism is configured to send,upon conclusion of the retraction mode of driving the spindle, apneumatic signal to the supply valve via the pneumatic circuit, thesupply valve being configured to move from the open position to theclosed position upon receiving the pneumatic signal, the pneumaticsignal deriving from a fixed quantity of air trapped at elevatedpressure within a reservoir located within the drive mechanism.
 2. Thedrilling machine of claim 1, wherein the pneumatic signal to the supplyvalve via the pneumatic circuit is a pneumatic signal sent directly tothe supply valve.
 3. The drilling machine of claim 1, the drivemechanism further including a coupling shaft for changing the mode ofdriving the driving mechanism, the coupling shaft being axially biasedby a coupling spring into a coupling chamber, the coupling chamber beingpositioned in the pneumatic circuit, wherein the reservoir includes thecoupling chamber.
 4. The drilling machine of claim 3, wherein thereservoir further includes a volume defined by a cycle counting device.5. The drilling machine of claim 3, wherein the drive mechanism isconfigured to expel a bolus of air from the reservoir under the bias ofthe coupling spring.
 6. The drilling machine of claim 3, wherein thepneumatic circuit includes a connector for receiving compressed air, thecontrol valve being configured in relation to the pneumatic circuit sothat, when the control valve is in the first position the couplingchamber is not open to the connector, but is open to the supply valve,via the pneumatic circuit.
 7. The drilling machine of claim 3, whereinthe pneumatic circuit includes a connector for receiving compressed air,the control valve being configured in relation to the pneumatic circuitso that, when the control valve is in the second position the couplingchamber is open to the connector, but is not open to the supply valve,via the pneumatic circuit.
 8. The drilling machine of claim 3, whereinthe drive mechanism further includes a cycle counter directly connectedvia the pneumatic circuit to the coupling chamber.
 9. The drillingmachine of claim 1, wherein the drive mechanism further includes a cyclecounter configured to add one count only upon commencement of theretraction mode of driving the spindle.
 10. The drilling machine ofclaim 1, the drive mechanism having a first condition at thecommencement of the driving cycle wherein the control valve is in thefirst position and the supply valve is closed, and a second condition atthe end of the driving cycle, the first condition being the same as thesecond condition.
 11. The drilling machine of claim 1, wherein the drivemechanism is configured to set the control valve in the first positionby a retraction movement of the spindle, and to set the control valve inthe second position by an advancing movement of the spindle.
 12. Thedrilling machine of claim 1, wherein the drive mechanism furtherincludes a manually operable valve configured in relation to thepneumatic circuit so that activation of the manually operable valvepneumatically moves the supply valve from the open position to theclosed position.